EP1621290B1 - Machine-outil avec impulsion intermittent - Google Patents

Machine-outil avec impulsion intermittent Download PDF

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Publication number
EP1621290B1
EP1621290B1 EP20050106953 EP05106953A EP1621290B1 EP 1621290 B1 EP1621290 B1 EP 1621290B1 EP 20050106953 EP20050106953 EP 20050106953 EP 05106953 A EP05106953 A EP 05106953A EP 1621290 B1 EP1621290 B1 EP 1621290B1
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EP
European Patent Office
Prior art keywords
hand
spindle
locking
machine tool
held machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP20050106953
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German (de)
English (en)
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EP1621290A1 (fr
Inventor
Hanspeter Schad
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilti AG
Original Assignee
Hilti AG
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Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
Publication of EP1621290A1 publication Critical patent/EP1621290A1/fr
Application granted granted Critical
Publication of EP1621290B1 publication Critical patent/EP1621290B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket

Definitions

  • the invention relates to a hand tool with a drive spindle, which can be acted upon by a motor with a drive torque.
  • the hand tool device has a tool spindle which serves to drive a tool bit in one direction of rotation.
  • the tool spindle on the one hand with the drive spindle can be coupled and on the other hand rotatably connected to a tool holder, to which the tool bit is attachable.
  • the hand tool device has a rotary pulse generator which, when a threshold value is reached with respect to a resistance moment occurring at the tool spindle, which is directed counter to the drive torque, subjects the latter to a recurring angular momentum.
  • such hand tool devices enable a change from a continuous to an intermittent rotary movement as soon as the braking forces occurring on the tool spindle and the tool holder produce a resistance moment which reaches the threshold value.
  • the tool spindle is subjected to very high recurring angular momenta, by which the moment of resistance can be more easily overcome and the work progress can be increased significantly.
  • a rotary impact tool in the form of a rotary impact wrench known.
  • This has a hammer element, which is engaged via balls with the drive spindle, which are guided both in the hammer element and on the drive spindle in oblique grooves. Furthermore, the hammer element on projections which can be applied in the rotational direction of projections of the tool spindle in order to transmit a torque from the drive spindle to the tool spindle.
  • the hammer element As soon as the moment of resistance, which is delivered by the screw to be screwed to the tool spindle, reaches a certain threshold when screwing, the hammer element is moved away from the tool spindle via the oblique grooves relative to the drive spindle until the projections of the hammer element out of engagement with the projections come the tool spindle and be moved past each other. It increases on the one hand by the lack of resistance to the projections, the rotational speed of the hammer element. In addition, the hammer element is accelerated by a tension spring acting on it in the direction of the tool spindle as soon as the projections have passed each other in the direction of rotation. In this way, the hammer element generates on the one hand on the tool spindle an axial contact pressure. On the other hand, the hammer element exerts blows on the tool spindle in the direction of rotation.
  • DE 43 44 849 shows a machine tool that switches over a certain moment of resistance from a quasi-continuous rotary motion with relatively low drive torque to a discontinuous rotary motion with relatively high recurring angular momentum both when screwing and core drilling.
  • the machine tool has an oscillating drive, which is coupled via a freewheel with the tool holder.
  • a disadvantage of the known hand tools is that they can not be used in a comfortable way for holes in the metal, at least.
  • the resistance moments occurring in the drilling area are namely not sufficient in normal operation to trigger the respective rotary pulse generator recurrently. Only by very strong pressing of the rotary impact tool against the metal to be processed, the threshold value of the resistance moment can be exceeded. This can be achieved in the metal drilling applications only by strong pressing of the hand tool by the operator a significantly increased Bohrvortrieb.
  • US 2,947,283 shows a pneumatic wrench with a cup-shaped output element, projects from an anvil element. This is repeatedly applied during operation by a hammer mechanism in the direction of rotation.
  • the output element is mounted with the interposition of a sliding bearing in a housing.
  • EP 1 182 010 describes a vibration generating motorized wrench. This has two mutually offset flywheels, one of which is rotatable about a tool spindle and acted upon by a braking device.
  • the present invention has for its object to avoid the disadvantages mentioned in a hand tool with rotary pulse generator and to allow a comfortable production of a metal hole.
  • the object is achieved in that on the tool spindle, a braking force generator is arranged, via which the tool spindle can be acted upon by a braking force acting counter to the direction of rotation.
  • a braking force generator is arranged, via which the tool spindle can be acted upon by a braking force acting counter to the direction of rotation.
  • the tool spindle can additionally be acted upon by the angular momentum generator with an axial force pulse.
  • the braking force generator automatically a recurrent pulse-like impact or contact force can be generated in the axial direction of the tool spindle, which occurs together with the angular momentum.
  • the angular momentum transmitted to the tool bit which is preferably designed as a metal drill, and which serves for shaving into the workpiece, is superimposed with a particularly high axial contact pressure. This results in a particularly good cutting of the drill into the workpiece, without the device must be pressed by the operator against the workpiece.
  • the braking force generator is optionally switched on and off.
  • the hand tool can be used as needed for either Tangentialglerschrauben or metal hammer drilling.
  • metal impact drilling can be provided as an additional, optionally switchable operating function on a Tangentialtschschraubêt.
  • the braking force generator has a sleeve-shaped carrier body, which is penetrated by the tool spindle.
  • the braking force can be applied circumferentially to the tool spindle, whereby a relatively large and uniform braking force can be generated.
  • a prestressed form friction fit can be produced between the carrier body and the tool spindle.
  • prestressed positive frictional engagement this means a frictional connection achieved by prestressing an element against a surface, which is reinforced by a quasi-form fit between the element and the surface.
  • this quasi-form closure only acts up to a certain holding force. In this way, it is possible to reliably apply a relatively high braking force to the tool spindle while at the same time reducing the wear on the braking force generator.
  • the mold friction is produced by a arranged between the carrier body and the tool spindle locking device.
  • This stores a locking body radially displaceable on one of the elements of the tool spindle and carrier body.
  • the latching body is biased against the respective other element, wherein at least one corresponding latching recess is recessed for receiving the latching body. In this way, a permanently constant braking force can be provided at a low manufacturing cost of the braking force generator.
  • the latching recess is formed by a groove extending transversely to the direction of rotation, whereby the latching device can be produced in a particularly simple and cost-effective manner.
  • the latching recess is advantageously formed by a Rampenaus simplifiedung having a spiral-shaped cross-section, wherein the depth of the Rampenaus simplifiedung in the direction of rotation increases steadily up to a paragraph, which acts as a stop for the locking body.
  • the latching body is initially pressed almost completely in the transverse bore when jumping from a first to a second latching position and gradually moved out of the transverse bore until the next stop position.
  • the latching recess is formed by a circular arc-shaped in cross section around the axis A, which has a constant depth in the direction of rotation over its length.
  • the locking body is over the entire angular range between the ribs or in a consistently maximally disengaged position relative to the transverse bore.
  • the contact pressure of the radial spring in this transition region is minimal, whereby the friction losses when jumping from one locking position to the next can be significantly reduced.
  • the carrier body between a braking position, in which the locking body is disposed at the axial height of the recesses, and a free-running position is advantageously displaceable, in which the locking body is arranged at the height of a rotating circumferential direction in the annular groove.
  • the latching device can be switched on and off in a simple manner.
  • the braking force generator can be switched on and off, depending on whether the hand tool is to be used as a tangential impact driver or as a percussion drill.
  • a frictional engagement can advantageously be produced between the carrier body and the tool spindle.
  • the braking force generator can be produced in a particularly cost-effective manner or its braking force can be increased without major effort.
  • the carrier body is formed by an elastic friction ring.
  • the braking force generator can be produced in a particularly cost-effective manner.
  • the threshold is in the range of 1 to 5 Nm.
  • This torque range has been found to be particularly suitable, since on the one hand ensures good performance of the rotary pulse generator and can be safely adjusted to the tool spindle with the above-mentioned braking force generators.
  • this value can certainly be surpassed by the drive torque of most tangential impact wrenches so that tangential impact wrenches with additional percussion drilling capability can be manufactured based on a production series of conventional tangential impact drills.
  • Fig. 1 shows a hand tool 2 in the form of a Tangentialtschschraubers having a housing 4, in which a universal motor 6 is housed.
  • the universal motor 6 drives a drive spindle 10 in the direction of rotation D about an axis A via a motor pinion 8.
  • the drive spindle 10 can be rotationally coupled to a tool spindle 14 via a rotary pulse generator, designated in its entirety by 12.
  • the tool spindle 14 is in turn rotatably connected to a tool holder 16 to which a tool bit 18, for example in the form of a screwdriver bit or a drill, in particular a metal drill, can be attached.
  • a braking force generator designated generally by 20 is provided, via which the tool spindle 14 can be acted upon by a braking force counter to the direction of rotation D.
  • the braking force generator 20 has a sleeve-shaped carrier body 22, which is penetrated by the tool spindle 14.
  • the carrier body 22 is displaceable in the axial direction but rotatably mounted in the housing 4.
  • a transverse to the axis A around the tool spindle 14 around circumferential annular groove 26 and two parallel to the axis A aligned recesses 28 are inserted, which open into the annular groove 26.
  • a radial spring 34 against the inner side 24 of the support body 22 and forms together with the recesses 28 and the annular groove 26 a total of 35 designated and disconnectable latching device.
  • Fig. 2 the rotary pulse generator 12 on a racket element 36 on which two racket projections 38 are formed, which protrude in the direction of the axis A.
  • the Schlagervorsprünge 38 are applied in the direction of rotation D to spindle projections 40 which project in the radial direction of the tool spindle 14, as indicated by dashed lines.
  • the racket element 36 is biased in the direction of the tool spindle 14 by means of an axial spring 42, which is supported on a bearing ring 44 fixedly connected to the drive spindle 10.
  • the axial spring has a spring stiffness of 10 3 to 10 5 N / m.
  • the beater element 36 is in contact with the drive spindle 10 via ball-shaped rotary drivers 46.
  • the rotary drivers 46 are guided on the one hand in a zigzag-shaped, circumferential cam groove 48, which is embedded in the drive spindle 10.
  • the rotary drivers 46 project partially into control recesses 50, which are embedded in an axial bore 52 of the racket element 36.
  • a drive torque M A is delivered from the drive spindle 10 to the rotary driver 46, which are pressed by the axial spring 42 both against the control groove 48 and against the respective control recess 50 initially in a fixed position.
  • the rotational drivers initially remain upon rotation of the drive spindle 10 and in this way transmit the drive torque M A to the racket element 36. From this, the drive torque M A on the Schlierervorsge 38 and the spindle projections 40 on the tool spindle 14 and from there to the Transfer tool holder 16.
  • the locking body 32 runs freely in the annular groove 26, so that no significant braking force acts on the tool spindle 14 of the braking force generator 20.
  • the braking force generator 20 is located in Fig. 2 thus in a freewheeling position, which are particularly suitable for driving screws and bolts, not shown, into a workpiece.
  • a resistance moment M B on the tool spindle 14 which is opposite to the drive torque M A , is generated via the tool bit 18 and the tool receptacle 16 which engage with the screw or the bolt.
  • this resistance moment M B reaches a threshold which is in a range of 1 to 5 Nm, the rotary drivers 46 can no longer be held in their fixed position, but move along with the racket element 36 along the cam 48 away from the tool spindle 14 , Here, the stroke of the bat member 36 is between 5 and 20mm. In this way, the racquet projections 38 come out of engagement with the spindle projections 40, so that they are moved in the direction of rotation D past each other. At the same time, the action of the resistance moment M B on the racket element 36 is interrupted.
  • the remaining beater element 36 is pressed by the axial spring 42 in the axial direction against the spindle projections 40.
  • the beater element 36 is accelerated along the control groove 48 in the direction of rotation D, so that the beater projections 38 are now beaten against the respective other spindle projection 40.
  • Fig. 3 shows the hand tool 2 in a Schlagbohrgna, which is particularly suitable for drilling metal, such as steel.
  • the support body 22 is displaced in the axial direction relative to the housing 4, that the locking body 32 is now biased at the level of the two recesses 28 against the inside 24.
  • the drive torque is transmitted from the drive spindle 10 via the rotary pulse generator 12 to the tool spindle 14.
  • the locking body 32 comes into engagement with one of the recesses 28.
  • the braking force generator 20 is located in Fig. 3 thus in a braking position, which is particularly suitable for drilling in metal.
  • the positive engagement between the latching body 32 and the respective latching recess 28 generates a braking force opposing the direction of rotation D, resulting in a resistance moment M B of from 1 to 5 Nm on the tool spindle 14.
  • the resistance element M B is sufficient to enable the angular momentum generator 12 to be in the beating state described above independently of the external forces acting on the tool bit 18.
  • the beater element 36 causes by the movement in the axial direction a pressing of the tool bit 18, which is used for this purpose in the form of a metal drill, against the respective workpiece to be machined. During this pressing operation, the beater element 36 also strikes with the beater projections 38 in the direction of rotation D against the spindle projections 40. As is apparent from the diagram Fig. 4 is apparent thereby in the direction of rotation D reaches an intermittent torque M of 300 Nm with a simultaneous short contact pressure F of about 1 kN. As a result, the tool bit 18 can cut particularly well into the workpiece without a person operating the hand tool 2 having to exert an increased contact pressure.
  • the Fig. 5a to 5c show a cross section through the braking force generator 20 for three different embodiments of the recesses 28a-c.
  • the positive engagement of the locking body 32 in the respective recess 28 is overcome only by the angular momentum generated by the rotary pulse generator 12.
  • the engagement body 32 is pressed against the radial spring 34 in the transverse bore 30 and the positive engagement repealed.
  • the locking body 32 thus jumps in operation with each angular momentum in the direction of rotation of the one locking recess 28 to the other.
  • the recesses 28a are formed by two opposing grooves 28a recessed into the inside 24, which are aligned parallel to the axis A. At these grooves, the locking body 32 in the direction of rotation D in operation produce a positive engagement with the rotationally fixed carrier body 22. When the locking body 32 is moved from one groove 28a to the other, it is almost completely pushed into the transverse bore 30 between two locking positions.
  • the locking recesses 28 are formed by two recessed into the inside 24 and in cross-section spiral ramp recesses 28b formed only in the direction of rotation D a paragraph 58 as a stop for the locking body 32.
  • the recesses 28 are formed by two in the inside 24 sunken and in cross-section arcuate recesses 28c. These form in the direction of rotation between two stop ribs 60, which act stop for the locking body 32. In this embodiment, it is ensured that the latching body 32 is pressed against the carrier body 22 with as little force as possible during the transition from the stop on the one stop rib 60 to the stop on the other stop rib 60.
  • the rotational strength of the carrier body 22 relative to the housing 4 is achieved by a rib 54 which engages in a corresponding receptacle 56 on the housing 4.
  • Fig. 6 shows the rotary pulse generator 12 together with another embodiment of the braking force generator 20 in an exploded view.
  • the carrier body 20 is formed by an elastic friction ring, for example made of rubber or plastic.
  • This friction ring is rotatably mounted in the housing 4 according to the above-mentioned carrier bodies 20 and generated by friction on the surface of the tool spindle 14, the necessary moment of resistance M B to trigger the rotary pulse generator 12.
  • braking force generators 20 could be made between the tool spindle 14 and the housing 4 a positive connection via a controlled locking member or a frictional connection via a controlled clamping member.
  • the control of the locking member or the clamping member could be carried out, for example, electromagnetic, piezoelectric, electrostrictive or magnetostrictive.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)

Claims (13)

  1. Appareil portatif (2) comprenant une broche d'entraînement (10) apte à être soumise par un moteur (6) à un couple d'entraînement (MA), comprenant une broche porte-outil (14) apte à être accouplée à la broche d'entraînement (10) pour entraîner un outil rapporté (18) dans un sens de rotation (D) et solidarisée en rotation à un raccord d'outil (16) sur lequel l'outil rapporté (18) peut être monté, et comprenant un générateur d'impulsions de rotation (12) qui, à l'atteinte d'une valeur de seuil applicable à un couple de résistance (MB) survenant au niveau de la broche porte-outil (14), soumet celle-ci à une impulsion de rotation, caractérisé en ce que sur la broche porte-outil (14) est disposé un générateur de force de freinage (20) par l'intermédiaire duquel la broche porte-outil (14) peut être soumise à une force de freinage agissant à l'opposé du sens de rotation (D), et en ce que le couple de résistance (MB) de la broche porte-outil (14) peut être accru indépendamment d'un couple de résistance extérieur.
  2. Appareil portatif selon la revendication 1, caractérisé en ce que la broche porte-outil (14) peut être soumise à une impulsion de force axiale par le générateur d'impulsions de rotation (12).
  3. Appareil portatif selon la revendication 1 ou 2, caractérisé en ce que le générateur de force de freinage (20) peut être mis en et hors circuit à volonté.
  4. Appareil portatif selon une des revendications 1 à 3, caractérisé en ce que le générateur de force de freinage (20) comporte un corps porteur (22) qui est monté solidaire en rotation et qui est traversé par la broche porte-outil (14).
  5. Appareil portatif selon la revendication 4, caractérisé en ce qu'une liaison précontrainte par friction et conjugaison de formes est réalisable entre le corps porteur (22) et la broche porte-outil (14).
  6. Appareil portatif selon la revendication 5, caractérisé en ce que la liaison par friction et conjugaison de formes est réalisable par l'intermédiaire d'un dispositif d'encliquetage (35) qui est disposé entre le corps porteur (22) et la broche porte-outil (14) et qui plaque un corps d'encliquetage (32) avec une possibilité de déplacement radial contre un élément constitué de la broche porte-outil (14) et du corps porteur (22), ledit corps d'encliquetage étant précontraint contre l'autre élément dans lequel est ménagé au moins un évidement d'encliquetage correspondant (28) pour recevoir le corps d'encliquetage (32).
  7. Appareil portatif selon la revendication 6, caractérisé en ce que l'évidement d'encliquetage (28) est formé par une rainure (28a) qui s'étend transversalement au sens de rotation (D).
  8. Appareil portatif selon la revendication 6, caractérisé en ce que l'évidement d'encliquetage (28) est formé par un évidement en rampe (28b) qui présente une section transversale spiralée, la profondeur de l'évidement en rampe (28b) croissant régulièrement dans le sens de rotation (D) jusqu'à un décrochement (58).
  9. Appareil portatif selon la revendication 6, caractérisé en ce que l'évidement d'encliquetage (28) est formé par un renfoncement à section transversale en arc de cercle (28c) qui est ménagé autour de l'axe A et qui présente une profondeur constante sur toute sa longueur.
  10. Appareil portatif selon une des revendications 6 à 9, caractérisé en ce que le corps porteur (22) est déplaçable entre une position de freinage, dans laquelle le corps d'encliquetage (32) est disposé à la hauteur axiale des évidements d'encliquetage (28), et une position de course libre, dans laquelle le corps d'encliquetage (32) est disposé à la hauteur d'une rainure annulaire (26) orientée dans le sens de rotation (D).
  11. Appareil portatif selon une des revendications 4 à 10, caractérisé en ce qu'une liaison par friction est réalisable entre le corps porteur (22) et la broche porte-outil (14).
  12. Appareil portatif selon la revendication 11, caractérisé en ce que le corps porteur (22) est formé par un anneau de friction élastique.
  13. Appareil portatif selon une des revendications 1 à 12, caractérisé en ce que le couple de seuil est compris entre 1 et 5 Nm.
EP20050106953 2004-07-30 2005-07-28 Machine-outil avec impulsion intermittent Ceased EP1621290B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200410037072 DE102004037072B3 (de) 2004-07-30 2004-07-30 Handwerkzeuggerät mit Drehimpuls- und Bremskrafterzeuger

Publications (2)

Publication Number Publication Date
EP1621290A1 EP1621290A1 (fr) 2006-02-01
EP1621290B1 true EP1621290B1 (fr) 2009-03-11

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Application Number Title Priority Date Filing Date
EP20050106953 Ceased EP1621290B1 (fr) 2004-07-30 2005-07-28 Machine-outil avec impulsion intermittent

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EP (1) EP1621290B1 (fr)
JP (1) JP2006043877A (fr)
DE (2) DE102004037072B3 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL2099584T3 (pl) * 2006-07-18 2018-01-31 Kistler Holding Ag Łączący zespół
CN201664908U (zh) 2007-06-15 2010-12-08 布莱克和戴克公司 混合冲击工具
US9193053B2 (en) 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
US8631880B2 (en) 2009-04-30 2014-01-21 Black & Decker Inc. Power tool with impact mechanism
US8460153B2 (en) 2009-12-23 2013-06-11 Black & Decker Inc. Hybrid impact tool with two-speed transmission
US8584770B2 (en) 2010-03-23 2013-11-19 Black & Decker Inc. Spindle bearing arrangement for a power tool
DE102011089910A1 (de) 2011-12-27 2013-06-27 Robert Bosch Gmbh Handwerkzeugvorrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2947283A (en) * 1955-02-04 1960-08-02 Earl G Roggenburk Impact tool
GB1407277A (en) * 1972-11-21 1975-09-24 Maurer S B Rotary power tool with centrifugal coupling means
DE4328599C2 (de) * 1992-08-25 1998-01-29 Makita Corp Rotations-Schlagwerkzeug
DE4344849A1 (de) * 1993-12-29 1995-07-06 Fein C & E Werkzeugmaschine
RU2182533C2 (ru) * 1998-04-03 2002-05-20 Стариков Иван Васильевич Вибрационный гайковерт

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Publication number Publication date
EP1621290A1 (fr) 2006-02-01
DE502005006791D1 (de) 2009-04-23
JP2006043877A (ja) 2006-02-16
DE102004037072B3 (de) 2006-01-12

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